EP1807640B1 - Continuously variable transmission provided with a control device - Google Patents
Continuously variable transmission provided with a control device Download PDFInfo
- Publication number
- EP1807640B1 EP1807640B1 EP04793677A EP04793677A EP1807640B1 EP 1807640 B1 EP1807640 B1 EP 1807640B1 EP 04793677 A EP04793677 A EP 04793677A EP 04793677 A EP04793677 A EP 04793677A EP 1807640 B1 EP1807640 B1 EP 1807640B1
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- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- line
- auxiliary
- pressure chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66254—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
- F16H61/66263—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using only hydraulical and mechanical sensing or control means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
Definitions
- these latter valves 161, 181 can be set in four main positions I-IV.
- a first position I of the valves 161, 181 the respective pressure chamber 7, 8 is allowed to communicate with he main line 12 for increasing the respective chamber pressure Ppri, Psec.
- a second position II of the valves 161, 181 the respective pressure chamber 7, 8 is closed-off for essentially maintaining the respective chamber pressure Ppri, Psec.
- a third position III of the valves 161, 181 the respective pressure chamber 7, 8 is allowed to communicate with the auxiliary line 14 for relieving the respective chamber pressure Ppri, Psec.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
Abstract
Description
- The present invention relates to a continuously variable transmission as defined in the preamble of the following
claim 1. - Such a continuously variable transmission and the control device applied therein are known from the
United States patent US 6,402,648 B1 . The known continuously variable transmission includes a primary or drive pulley and a secondary or driven pulley, as well as an endless transmission element, which may be one of several known types, wrapped around and in frictional contact with the said pulleys. The transmission provides a transmission speed ratio between the drive and the driven pulleys that may be controlled to an arbitrary value within a range of transmission ratios covered by said transmission by an appropriate actuation thereof, which actuation is commonly effected by a control device of the transmission. - The known control device includes two pressure chambers; each associated with a respective pulley for effecting a respective clamping force on the endless transmission element. To this end, the control device includes a hydraulic pump and at least five hydraulic circuit parts wherein different pressure levels prevail. The pump supplies a flow of hydraulic fluid from a first circuit part or oil sump, wherein the lowest pressure level, normally the ambient pressure, prevails, to a second circuit part or main line, wherein the highest pressure level in the system prevails. The highest prevailing pressure, the so-called line pressure, is hereby set by means of a line pressure control valve, which valve discharges a surplus pump flow into a third circuit part or auxiliary line, where the prevailing pressure, the so-called auxiliary pressure, is set by means of a further pressure control valve. From the auxiliary line several auxiliary hydraulic users are supplied with fluid, such as a torque converter or lubrication points of the transmission. Further, fourth and fifth circuit parts are provided, respectively associated with the pressure chamber of the primary pulley and of the secondary pulley. Both said circuit parts are connectable to and can be supplied with pressurised fluid from the main line, via hydraulic valves, i.e. the primary valve and the secondary valve respectively. These latter valves are also used to respectively relieve the pressure in the primary pressure chamber, or primary pressure for short, and in the secondary pressure chamber, or secondary pressure for short, by selectively providing a hydraulic connection between such pressure chamber and the auxiliary line.
- Although the above-described known control device should function satisfactorily per se and, in principle, is able to provide a relatively energy efficient actuation of the transmission, it also comes with the limitation that the primary pressure and the secondary pressure are at least equal to the auxiliary pressure, which normally is maintained at a level of at least 4 to 5 bar. The pulley will thus always exert an appreciable clamping force on the endless transmission element, even in conditions where such is not desirable for at least one pulley, e.g. when only a very small or no driving power at all is to be transmitted by the transmission (e.g. in vehicle coasting conditions), or when the transmission speed ratio is to be changed rapidly (e.g. in vehicle emergency stop conditions).
- Departing from the known control device the present invention aims at further improving the functionality and efficiency thereof, while maintaining its favourable features in relation to the actuation of the continuously variable transmission.
- According to the invention such aim may be achieved with the transmission construction according to the
claim 1 attached hereto. More specifically, according to the invention the control device comprises valve means that, in order to re lieve the pressure in a at least one of the pressure chambers, can selectively connected that pressure chamber to either the auxiliary line -to conserve hydraulic power-, or to the oil sump -to enhance transmission functionality-. To this end, the control device may comprise a further valve that connects the respective pressure chamber to an intermediate hydraulic line of the valve means when relieving the pressure prevailing therein, whereby the valve means comprise a further valve, e.g. a switch valve, for selectively connecting such intermediate line to either the auxiliary line or to the oil sump. - The invention, in a further elaboration, also relates to an embodiment of the valve means wherein they are integrated with the further valve, which embodiment is specifically adapted to be applied in the control device according to the invention and that favourably obviates the use of the above-mentioned separate switch valve and intermediate hydraulic line. This further valve comprises four hydraulic connections, whereof one is linked to the main line, one to the respective pressure chamber, one to the auxiliary line and one to the oil sump, whereby the connection to the auxiliary line incorporates a simple one-way or check valve. With this design of the further valve a hydraulic connection is provided between the respective pressure chamber and either the auxiliary line alone, or both the auxiliary line and the oil sump, whereby the check valve closes off the auxiliary line when the chamber pressure drops below the auxiliary pressure. Hereby, a relatively compact valve design is provided that requires a less strict manufacturing tolerance and, during operation, provides a smooth pressure relieve, also at the instant where the hydraulic connection of the pressure chamber is switched from the auxiliary line to the oil sump.
- The invention will now be elucidated further along a drawing in which:
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figure 1 is a diagrammatic representation of a prior art and to be improved control device as a part of a schematically depicted continuously variable transmission that is to be actuated thereby; -
figure 2 represents a first possible configuration of the novel transmission according to the invention; -
figures 3, 4 and 5 each are a schematic cross section of an embodiment of the secondary valve that is particularly suited for application in the transmission according the invention; -
figure 6 is a schematic cross section of a primary valve that is particularly suited for application in the transmission according the invention; -
figure 7 represents a second possible configuration of the novel transmission according to the invention; and -
figure 8 represents a third possible configuration of the novel transmission according to the invention. - In the figures, identical references relate to corresponding technical functions or structures, as the case may be. The thick lines indicate hydraulic lines, i.e. passages for hydraulic medium, whereas the dashed lines indicate pressure control lines for the control, i.e. the biasing of the various hydraulic valves.
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Figure 1 schematically shows a continuouslyvariable transmission 1, for realising and changing a physical transmission ratio between an input orprimary shaft 2 and an output orsecondary shaft 3 of thetransmission 1 comprising a control device for the actuation of thetransmission 1, including any auxiliary functions thereof. Such auxiliary functions are represented by hydraulic users U1, U2, such as a clutch or a lubrication point of thetransmission 1. Thetransmission 1 may be incorporated between an engine E and a load L, for example in a motor vehicle, for varying a speed and torque transmission ratio between the engine E and the load L within a continuous range of possible transmission ratios. - In this particular illustrative example the
transmission 1 comprises an endlessflexible belt 4 that is wrapped around and between a primary pulley 5 placed on theprimary shaft 2 and secondary pulley 6 placed on thesecondary shaft 3. Thebelt 4 is frictionally engaged with the pulley discs of the respective pulleys 5, 6 by means of clamping forces, respectively generated by a hydraulic pressure exerted in aprimary pressure chamber 7 associated with an axially moveable disc of theprimary pulley 2, i.e. the primary pressure Ppri, and by a hydraulic pressure exerted in asecondary pressure chamber 8 associated with an axially moveable disc of thesecondary pulley 3, i.e. the secondary pressure Psec. - These pressures Ppri, Psec are set by the control device, which to this end comprises a
pump 10 that normally is driven directly and continuously by the engine E and supplies a flow of pressurised hydraulic medium to amain line 12 of a hydraulic circuit, whereby such medium is drawn from areservoir 11 for hydraulic medium, oroil sump 11. The pressure level in thismain line 12, i.e. the line pressure Pline, is controlled by aline pressure valve 13, possibly to a fixed pressure level that is slightly higher than the highest level of the primary pressure Ppri and the secondary pressure Psec that is required during operation of thetransmission 1, but usually to a level that is slightly (e.g. 0,5 to 2 bar) higher than the highest of the instantaneous primary and secondary pressure level Ppri, Psec. To this end, theline pressure valve 13 is provided with generally known valve biasing means 13a, 13b and 13c, being apressure feedback line 13a, aspring 13b and acontrol line 13c. By means of an electronic control unit or ECU (not shown) and an associated solenoid valve (not shown) the pressure in thecontrol line 13c is set, so that, in turn, a desired line pressure Pline is realised during operation of thetransmission 1. - The
line pressure valve 13 discharges a surplus of the pump flow into an auxiliaryhydraulic line 14 from which the auxiliary hydraulic users U1, U2 of thetransmission 1 are fed with hydraulic medium. The pressure level in thisauxiliary line 14, i.e. the auxiliary pressure Paux, is controlled by anauxiliary pressure valve 15, usually to a fixed, relatively low pressure level of a few (e.g. 5) bar. To this e nd, theauxiliary pressure valve 15 is provided with apressure feedback line 15a and aspring 15b. Theauxiliary pressure valve 15 discharges a remaining surplus of the pump flow into theoil sump 11. - The primary pressure Ppri is controlled by means of a further, or
primary pressure valve 16 via a first intermediatehydraulic line 17 connected to theprimary pressure chamber 7. Theprimary pressure valve 16 further comprises hydraulic connections to themain line 12 and theauxiliary line 14 and is thus capable of selectively allowing theprimary pressure chamber 7 to communicate with he mainline 12 for increasing the primary pressure Ppri, or to theauxiliary line 14 for relieving the primary pressure Ppri. To this end, theprimary pressure valve 1 6 is provided with apressure feedback line 16a, aspring 16b and acontrol line 16c. By means of the ECU (not shown) and an associated solenoid valve (not shown) the pressure in thelatter control line 16c is set, so that, in turn, a desired primary pressure Ppri may be realised reliably during operation of thetransmission 1. - The secondary pressure Psec is controlled in an analogous manner by means of yet a further, or
secondary pressure valve 18 via a second intermediatehydraulic line 19 connected to thesecondary pressure chamber 8. Thesecondary pressure valve 18 further comprises hydraulic connections to themain line 12 and theauxiliary line 14 and is thus capable of selectively allowing thesecondary pressure chamber 8 to communicate with he mainline 12 for increasing the secondary pressure Psec, or to theauxiliary line 14 for relieving the secondary pressure Psec. To this end, thesecondary pressure valve 18 is provided with apressure feedback line 18a, aspring 18b and acontrol line 18c. By means of the ECU (not shown) and an associated solenoid valve (not shown) the pressure in thelatter control line 18c is set, so that, in turn, a desired secondary pressure Psec may be realised reliably during operation of thetransmission 1. - Accordingly with this known control device, both the minimum level of the primary pressure Ppri and of the secondary pressure Psec are limited to the auxiliary pressure level Paux. However, as mentioned in the above, during operation of the
transmission 1 operational conditions can occur such wherein it would be favourable if the primary pressure Ppri, or the secondary pressure Psec could be relieved towards theoil sump 11. - In
figure 2 a first possible configuration of the control device according to the present invention is illustrated, which maintains the favourable features of the known device and which at the same time provides the advantage that the pressure prevailing in thepressure chambers auxiliary line 14, or to theoil sump 11. The control device offig ure 2 is of similar configuration and operation as that offigure 1 , however, with the exception of theprimary pressure valve 161 and thesecondary pressure valve 181. - In accordance with the present invention, these
latter valves valves respective pressure chamber line 12 for increasing the respective chamber pressure Ppri, Psec. In a second position II of thevalves respective pressure chamber valves respective pressure chamber auxiliary line 14 for relieving the respective chamber pressure Ppri, Psec. In a fourth position IV of thevalves respective pressure chamber oil sump 11 for relieving the respective chamber pressure Ppri, Psec even further, possibly even to the ambient pressu re level. With this valve arrangement and the appropriate activation thereof by mean s of the ECU (not shown) and the associated solenoid valves (not shown) the general aim of the present invention may thus be achieved. - In the
figure 3 a possible embodiment of thesecondary valve 181 is illustrated in greater detail in a cross-section. The valve design shown infigure 3 may in principle be applied both as theprimary valve 161 and as thesecondary valve 181 in the hydraulic configuration of the control device according tofigure 2 , but is described hereunder with reference to the hydraulic connections of thesecondary valve 181. Thevalve 181 comprises ahousing 182 and avalve body 183 of predominantly cylindrical shape and provided axially moveable within thehousing 182. The position of thevalve body 183 in such axial direction is determined by valve biasing means 185, 186 in the form of aspring 185 that effects a first force on thevalve body 1 83 urging it towards the right, which spring force is balanced by a second, variable force urging thevalve body 183 towards the left, which second force is effected by a valve control pressure Psol in thecontrol line 186 that is set by means of the ECU (not shown) and an associated solenoid valve (not shown). - The
housing 182 provides one hydraulic connection to themain line 12, one to therespective pressure chamber 8 via the respectiveintermediate line 19, one to theauxiliary line 14 and one to theoil sump 11. The design of thevalve body 183, in particular of recessedsections 184 thereof, is such that as thevalve body 183 axially moves from its rightmost position in thevalve housing 182 towards the right under the influence of an increasing valve control pressure Psol, it sequentially opens and closes the fluid communication between the respectiveintermediate line 19 and themain line 12, theauxiliary line 14 and theoil sump 11. Thisvalve 181 is thus capable of allowing therespective pressure chamber 8 to communicate with hemain line 12 for increasing the secondary pressure Psec, or selectively with theauxiliary line 14 or theoil sump 11 for relieving the secondary pressure Psec, as is required for the present invention. - However, when applying the above-described valve embodiment problems may be encountered in that it has a considerable (axial) dimension and that very narrow tolerances need to be applied at manufacture. These problems are mainly caused by the fact that, on the one hand, a leaking of hydraulic medium from the
auxiliary line 14 to theoil sump 11 through therespective valve 181 obviously needs to be effectively prevented, whereas, on the other hand, a smooth transition needs to be realised between the above-mentioned third position III and the fourth position IV of thevalve body 183, preferably without interrupting or the flow of hydraulic fluid from therespective pressure chamber 8. These functional requirements result in contradictory structural requirements on the valve design, which can at best only be approximated and, moreover, at considerable effort and expense in manufacturing. - The present invention, therefore, further relates to a valve embodiment that satisfies the above-mentioned functional requirements and, moreover, can be manufactured relatively easily. This valve embodiment is shown in the cross-section of
figure 4 . In this embodiment thevalve body 183, in its right most position, opens the fluid communication between the respectiveintermediate line 19 and, sequentially, both theauxiliary line 14 and theoil sump 11, whereby a one-way, orcheck valve 187 is provided in theauxiliary line 14 to prevent leakage of hydraulic fluid from thisline 14 into theoil sump 11. In this embodiment, it is thus advantageously not relied on thevalve body 183 to close off the fluid communication between theauxiliary line 14 and theoil sump 11. - Although this latter valve embodiment of
figure 4 is a considerable improvement over the valve embodi ment offigure 3 , it also comes with the disadvantage that the axial movement of thevalve body 183 between it leftmost and rightmost positions within thehousing 182 is relatively large, because of the axial separation between the connection to theauxiliary line 14 and theoil sump 11, that are sequentially opened or closed by the axial movement of thevalve body 183. This makes it difficult to rapidly change between pressure relieve to pressurisation of the respective primary or secondary pressure Ppri, Psec or vice versa. - The present invention, therefore, further relates to a valve embodiment wherein the axial movement of the valve body is favourably minimised, which valve embodiment is shown in the cross-section of
figure 5 . In this embodiment thevalve body 183 is provided with a first and asecond recess housing 182 is provided with aninternal recess 189 adjacent to its hydraulic connection to theauxiliary line 11 and facing thevalve body 183. This valve design allows thevalve body 183, as it moves towards the left, to open the fluid communication between the respectiveintermediate line 19 and theoil sump 11 immediately after the fluid communication to theauxiliary line 14 is opened. Hereby, the fluid flows from respectiveintermediate line 19, through all of the above-mentionedrecesses oil sump 11, whereby, again the check-valve 187 prevents leakage of hydraulic fluid from thisauxiliary line 14. - A further feature introduced in the valve embodiment of
figure 5 is inclusion of a feedback of the respective primary or secondary pressure Ppri, Psec, via theinternal line 190, in the valve biasing means 185, 186, 190. Such feature and its advantages are, however, commonly known and applied in the art. However, specifically in case ofprimary valve 161, the invention proposes to not only include pressure feedback of the primary pressure Ppri itself, but also from the secondary pressure Psec. That is to further extend the valve biasing means 185, 186, 190, 191 by a furtherinternal line 191 for allowing the secondary pressure Psec to act on thevalve body 183, as is indicated in the cross-section offigure 6 . This valve embodiment is, according to the invention, particularly suited for application in the known control device, because apart from the above-explained features and advantages it also provides a favourable and automatic dependency of the primary pressu re Ppri on the secondary pressure Psec. Such dependency being favourable because when the secondary pressure Psec is raised or lowered, e.g. due to, respectively, an increased or a reduced engine torque, in an accurately controlled manner by the ECU based on the actually measured secondary pressure Psec, the primary pressure Ppri automatically follows such change. Thus, also the primary pressure Ppri may be accurately controlled by the ECU, however, favourably without having to actually measure the primary pressure Ppri. - In
figure 7 a second possible configuration of the control device according to the present invention is illustrated, which control device is of similar configuration and operation as that offigure 2 , however, with the exception of the operation of theauxiliary pressure valve 15 and that of theline pressure valve 13, i.e. of the respective valve biasing means 13a, 13b, 13c, 15a, 15b and 15c thereof. - In relation to the operation of the
auxiliary pressure valve 15 it is remarked that, according to the present invention, the efficiency of thetransmission 1 may be enhanced even further when the control device is arranged such that the auxiliary pressure Paux is made variable, for example under the influence of a control pressure in acontrol line 15c of theauxiliary valve 15, as indicated in thefigure 7 . - This feature opens up the possibility to temporarily lower the auxiliary pressure Paux to below the above-mentioned normal level of 4- to 5 bar, so that hydraulic fluid from a
pressure chamber auxiliary line 14, even when the respective primary or secondary pressure Ppri, Psec is to be relieved to such lower level. According to the invention such lowering of the auxiliary pressure Paux is generally allowable without endangering the auxiliary functions thereof, because such low level of the primary or secondary pressure Ppri, Psec, i.e. lower than the normal level of the auxiliary pressure Paux, will typically occur when a very small or no driving power at all is to be transmitted by the transmission 1 (i.e. said vehicle coasting and/or emergency stop conditions). It being obvious that in such circumstance, the above-mentioned auxiliary users of the lubrication points and the clutch require less flow of hydraulic medium and/or at a lower pressure level for their proper operation. - The control pressure in the
control line 15c of theauxiliary valve 15 may be specifically set for this purpose, e.g. by means of the ECU and an associated solenoid valves, or may be an appropriate pressure level prevailing in the control device, e.g. a further control pressure used to influence a clutch engagement pressure valve (not shown) for clutch engagement control. - Of course, this latter feature of the variable auxiliary pressure Paux may be favourably applied in the known transmission as such, i.e. apart from the above-described valve arrangement according to the invention. However, applying both features in the control device simultaneously will further enhance efficiency.
- In relation to the operation of the
line pressure valve 13 it is remarked that, according to the present invention, the control device may be simplified by allowing the highest of the primary pressure Ppri and the secondary pressure Psec to bias theline pressure valve 13 via itscontrol line 13c. To this end, thiscontrol line 13c is hydraulically connected -lines primary pressure chamber 7 and thesecondary pressure chamber 8, whereby, however, asimple switch valve 20 is provided insuch connection lines pressure chamber line pressure valve 13 are mutually adapted so that the line pressure Pline will be maintained at a level that is slightly (e.g. 0,5 to 2 ba r) higher than the highest of the instantaneous primary and secondary pressure level Ppri, Psec. Hereby, the above-mentioned control of theline pressure valve 13 by means of the ECU and the associated solenoid valve may be favourably omitted in a cost effective way. - Alternatively, it may be opted not to allow the highest of the actual primary pressure Ppri and the actual secondary pressure Psec to bias the
line pressure valve 13 via itscontrol line 13c as described above, but rather to use the -control- pressure in thecontrol line respective valve - Of course, this latter feature of the operation or, more in particular, the biasing of the
line pressure valve 13 may be favourably applied in the known transmission as such, i.e. apart from the above-described valve arrangement and/or variable auxiliary pressure Paux feature according to the invention. However, applying all of these features in the control device simultaneously will provide optimal results. - In
figure 8 a third possible configuration of the control device according to the present invention is illustrated, which control device is of a different hydraulic configuration and operation as that offigures 1, 2 and7 , which illustrates that the application of the present invention is not limited to the particular hydraulic layout of the control device described herein-above. In the control device shown infigure 8 , which is well known per se, the secondary pressure Psec is directly controlled by means of theline pressure valve 13. In this configuration, the secondary pressure Psec is identical to the line pressure Pline and the further, i.e. additional,secondary pressure valve 181 is thus not required. - In this configuration, in accordance with the present invention, in the
primary pressure valve 161 is arranged such that is capable of relieving the primary pressure Ppri by allowing theprimary pressure chamber 7 to communicate selectively with theauxiliary line 14 or with theoil sump 11. With this arrangement of theprimary pressure valve 161 and the appropriate activation thereof by means of the ECU (not shown) and the associated solenoid valves (not shown) the general aim of the present invention may thus be achieved.
Claims (10)
- Continuously variable transmission (1) with a control device comprising a pump (10) for supplying a flow of pressurised hydraulic medium to a main line (12) of the device, whereby such medium is drawn from an oil sump (11), a line pressure valve (13) for controlling the pressure level (Pline) in the main line (12), which latter valve (13) discharges a surplus of the pump flow into an auxiliary hydraulic line (14) of the device, an auxiliary pressure valve (15) for controlling the pressure level (Paux) in the auxiliary line (14) and a pressure chamber (7, 8) that is accociated with an axially moveable disc of a pulley (5, 6) of the continuously variable transmission (1), characterised in that, the device is further provided with valve means (161, 181) for selectively providing a hydraulic connection between the pressure chamber (7; 8) and the oil sump (11) or between the pressure chamber (7; 8) and the auxiliary line (14).
- Continuously variable transmission (1) according to claim 1, characterised in that the valve means (161, 181) are integrated in a further valve (161, 181) for controlling the pressure level (Ppri, Psec) in the pressure chamber (7).
- Continuously variable transmission (1) according to claim 2, characterised in that the further valve (161, 181) comprises four hydraulic connections, whereof one is linked to the main line (12), one to the pressure chamber (7, 8), one to the auxiliary line (14) and one to the oil sump (11) and whereby the further valve (161, 181) is capable of selectively opening a hydraulic connection of the pressure chamber (7; 8) either to the main line (12), to the auxiliary line (14), or to the oil sump (11).
- Continuously variable transmission (1) according to claim 2, characterised in that the further valve (161, 181) comprises four hydraulic connections, whereof one is linked to the main line (12), one to the pressure chamber (7, 8), one to the auxiliary line (14) and one to the oil sump (11), whereby the connection to the auxiliary line (14) incorporates a check valve (187) and whereby the further valve (161, 181) is capable of selectively opening a hydraulic connection of the pressure chamber (7; 8) either to the main line (12), to the auxiliary line (14), or to both the auxiliary line (14) and the oil sump (11).
- Continuously variable transmission (1) according to claim 4, characterised in that the further valve (161, 181) comprises a housing (182), wherein the said hydraulic connections are provided, and a valve body (183) provided axially moveable within the housing (182), whereby the valve body (183) is provided with first and second recesses (184, 188) and whereby the housing (182) is provided with an internal recess (189) adjacent to the hydraulic connection to the auxiliary line (11) and facing the valve body (183).
- Continuously variable transmission (1) according to any one of the claims 2 to 5, characterised in that the further valve (161, 181) comprises a valve body (183) provided axially moveable within a respective housing (182) and an internal line (190) allowing hydraulic fluid pressurised at the pressure level (Ppri, Psec) of the respective pressure chamber (7, 8) associated with the further valve (161, 181) to act on the said valve body (183).
- Continuously variable transmission (1) according to claim 6, characterised in that the further valve (161, 181) is provided with a further internal line (191) allowing hydraulic fluid pressurised at the pressure level (Ppri, Psec) of the respective other pressure chamber (7, 8) not associated with the further valve (161, 181) to act on the said valve body (183).
- Continuously variable transmission (1) according to any one of the preceding claims, characterised in that the respective pressure chamber (7, 8) is associated with an axially moveable disc of a primary pulley (2) of the transmission (1) that is to be driven by the engine (E) of a motor vehicle.
- Continuously variable transmission (1) according to any one of the preceding claims, characterised in that the auxiliary pressure (Paux) is variable.
- Continuously variable transmission (1) according to claim 9, characterised in that the auxiliary pressure valve (15) is provided with valve biasing means (15a, 15b, 15c) including a control line (15c) carrying fluid pressurised at a pressure level prevailing elsewhere in the control device.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/NL2004/000753 WO2006046849A1 (en) | 2004-10-27 | 2004-10-27 | Continuously variable transmission provided with a control device |
Publications (2)
Publication Number | Publication Date |
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EP1807640A1 EP1807640A1 (en) | 2007-07-18 |
EP1807640B1 true EP1807640B1 (en) | 2008-03-05 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP04793677A Not-in-force EP1807640B1 (en) | 2004-10-27 | 2004-10-27 | Continuously variable transmission provided with a control device |
Country Status (6)
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EP (1) | EP1807640B1 (en) |
JP (1) | JP4857275B2 (en) |
CN (1) | CN100491777C (en) |
AT (1) | ATE388355T1 (en) |
DE (1) | DE602004012337T2 (en) |
WO (1) | WO2006046849A1 (en) |
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JP4955598B2 (en) * | 2008-03-28 | 2012-06-20 | 富士重工業株式会社 | Control device for continuously variable transmission |
WO2014148124A1 (en) * | 2013-03-22 | 2014-09-25 | ジヤトコ株式会社 | Control device for belt-type continuously variable transmission |
CN107061671A (en) * | 2017-03-29 | 2017-08-18 | 湖南江麓容大车辆传动股份有限公司 | A kind of buncher hydraulic system |
CN110847859B (en) * | 2019-11-11 | 2021-09-14 | 中国海洋石油集团有限公司 | Intelligent well completion downhole flow valve ground control ultrahigh pressure hydraulic system |
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---|---|---|---|---|
JPS58203260A (en) * | 1982-05-21 | 1983-11-26 | Toyota Motor Corp | Oil pressure controller of stepless transmission gear |
JPH0765662B2 (en) * | 1986-12-26 | 1995-07-19 | トヨタ自動車株式会社 | Hydraulic control device for vehicle belt type continuously variable transmission |
DE4039830C1 (en) * | 1990-12-13 | 1992-01-16 | P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De | Variable transmission with V-belt - incorporates hydraulic system for controlling setting of conical pulleys |
CN2284318Y (en) * | 1996-12-12 | 1998-06-17 | 秦润祥 | Hydraulic driving stageless speed variator |
DE10021793B4 (en) * | 1999-05-14 | 2010-05-20 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Device for controlling CVT transmissions |
US6290620B1 (en) * | 1999-06-25 | 2001-09-18 | Hamilton Sundstrand Corporation | Continuously variable transmission with control arrangement and method for reducing impact of shock load |
DE19934698A1 (en) | 1999-07-23 | 2001-01-25 | Zahnradfabrik Friedrichshafen | Device for controlling continuous automatic gearbox feeds leakage gas directly into hydraulic constant pressure circuit, e.g. secondary circuit for supplying hydrodynamic converter |
-
2004
- 2004-10-27 JP JP2007538838A patent/JP4857275B2/en not_active Expired - Fee Related
- 2004-10-27 AT AT04793677T patent/ATE388355T1/en not_active IP Right Cessation
- 2004-10-27 CN CNB2004800443023A patent/CN100491777C/en not_active Expired - Fee Related
- 2004-10-27 EP EP04793677A patent/EP1807640B1/en not_active Not-in-force
- 2004-10-27 WO PCT/NL2004/000753 patent/WO2006046849A1/en active Application Filing
- 2004-10-27 DE DE602004012337T patent/DE602004012337T2/en active Active
Also Published As
Publication number | Publication date |
---|---|
CN101052830A (en) | 2007-10-10 |
JP4857275B2 (en) | 2012-01-18 |
CN100491777C (en) | 2009-05-27 |
ATE388355T1 (en) | 2008-03-15 |
EP1807640A1 (en) | 2007-07-18 |
DE602004012337D1 (en) | 2008-04-17 |
DE602004012337T2 (en) | 2009-03-12 |
WO2006046849A1 (en) | 2006-05-04 |
JP2008518176A (en) | 2008-05-29 |
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